US6397692B1 - Electro-mechanical automatic transmission for front wheel drive - Google Patents
Electro-mechanical automatic transmission for front wheel drive Download PDFInfo
- Publication number
- US6397692B1 US6397692B1 US09/506,965 US50696500A US6397692B1 US 6397692 B1 US6397692 B1 US 6397692B1 US 50696500 A US50696500 A US 50696500A US 6397692 B1 US6397692 B1 US 6397692B1
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- Prior art keywords
- shaft
- gears
- input shaft
- gear
- input
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- Expired - Lifetime
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/10—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with one or more one-way clutches as an essential feature
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
- F16H2003/0938—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts with multiple gears on the input shaft directly meshing with respective gears on the output shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0047—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising five forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
- Y10T74/19233—Plurality of counter shafts
Definitions
- the present invention relates to an automatic transmission, and more particularly, to an electro-mechanical automatic transmission having dual input shafts.
- the first, and oldest, type of powertrain is the manually operated powertrain.
- These powertrains are typically characterized in that vehicles having manual transmissions include a clutch pedal to the left of a brake pedal and a gear shift lever which is usually mounted at the center of the vehicle just behind the dashboard.
- the driver To operate the manual transmission, the driver must coordinate depression of the clutch and accelerator pedals with the position of the shift lever in order to select the desired gear.
- Proper operation of a manual transmission is well known to those skilled in the art, and will not be described further herein.
- Automatic and manual transmissions offer various competing advantages and disadvantages.
- a primary advantage of a manual transmission is improved fuel economy.
- automatic transmissions first and foremost offer easy operation, so that the driver need not burden both hands, one for the steering wheel and one for the gear shifter, and both feet, one for the clutch and one for the accelerator and brake pedal, while driving.
- the driver When operating a manual transmission, the driver has both one hand and one foot free.
- an automatic transmission provides extreme convenience in stop and go situations, as the driver need not worry about continuously shifting gears to adjust to the ever-changing speed of traffic.
- synchronization is obtained in a manual transmission by way of a synchronizing mechanism such as a mechanical synchronizer which is well known in the art.
- the mechanical synchronizer varies the speed of the driveshaft to match the speed of the driven shaft to enable smooth engagement of the selected gear set. For example, during an upshift, the mechanical synchronizer utilizes frictional forces to decrease the rate of rotation of the driveshaft so that the desired gear of the driveshaft is engaged smoothly to drive the desired gear of the driven shaft.
- the mechanical synchronizer increases the rate of rotation of the driveshaft so that the desired gear is engaged smoothly to drive the desired gear on the driven shaft.
- the clutch connection between the engine output shaft and the transmission input shaft needs to be disengaged prior to the gear shifting process and re-engaged upon synchronization.
- the electro-mechanical automatic transmission of the present invention is essentially an automated manual transmission.
- the design utilizes a dual clutch/dual input shaft layout.
- the layout is the equivalent of having two transmissions in one housing. Each transmission can be shifted and clutched independently. Uninterrupted power upshifting and downshifting between gears is available along with the high mechanical efficiency of a manual transmission being available in an automatic transmission. Significant increases in fuel economy and vehicle performance are achieved.
- the present invention is directed to an electro-mechanical automatic transmission for use with a front wheel drive vehicle. A similar design for a rear wheel drive vehicle is disclosed in commonly assigned U.S. Pat. No. 5,966,989 which is herein incorporated by reference.
- an electro-mechanical automatic transmission including a first input shaft and a second input shaft concentric with the first input shaft.
- a plurality of drive gears are rotatably mounted to the first input shaft.
- An idler gear is provided in meshing engagement with an input gear on said second input shaft.
- the idler gear drives a lay shaft which is also provided with a plurality of drive gears rotatably mounted thereon.
- the first input shaft and the lay shaft are provided with synchronizer devices for selectively engaging the drive gears thereto.
- a driven shaft is provided with a plurality of driven gears in meshing engagement with the drive gears.
- the electro-mechanical automatic transmission is provided with a pair of electro-mechanical clutch actuators for selectively disengaging dual clutches which transmit engine torque to the input shafts, as well as an electro-mechanical shift actuator system which operatively engage the synchronizer devices for selectively engaging the drive gears.
- the dual clutch system of the present invention includes two dry discs driven by a common flywheel assembly.
- Two electro-mechanical clutch actuators are provided to control disengagement of the two-clutch discs independently. Shifts are accomplished by engaging the desired gear prior to a shift event and subsequently engaging the corresponding clutch.
- the transmission of the present invention can be in two different gear ratios at once, but only one clutch will be engaged and transmitting power.
- the driving clutch will be released and the released clutch will be engaged.
- the two-clutch actuators perform a quick and smooth shift as directed by an on-board vehicle control system using closed-loop control reading engine RPMs or torque.
- the transmission shaft that is disengaged will then be shifted into the next gear ratio in anticipation of the next shift.
- a hill holder mechanism is provided in the form of an engagable overruning one-way roller clutch. This clutch will be engaged when the transmission is in first, second, or third gears in order to prevent vehicle rollback on a hill.
- a series of four synchronizer pairs are preferably used on one of the input shafts and a lay shaft.
- the hill holder mechanism is selectively engaged by one of the synchronizers.
- the hill holder prevents rollback of the vehicle when it is stopped. Contrary to an automatic transmission, there is no engine torque required to hold the vehicle from rolling back on a grade, thus efficiency is improved.
- the transmission of the present invention includes drive gears on a first and a second shaft in meshing engagement with common driven gears on the output shaft.
- the ability to utilize a single driven gear to mate with two different drive gears on the first and second shafts allow for the reduction of the number of gears and a reduction in size of the transmission.
- the shortened length of the transmission permits the transmission to be utilized in a transaxle powertrain.
- FIG. 1 is a sectional view of the electro-mechanical automatic transmission according to the principles of the present invention
- FIG. 2 illustrates the layout of the various shafts of the electro-mechanical automatic transmission for a front wheel drive vehicle according to the principles of the present invention
- FIG. 3 is a schematic illustration of the control system for the electro-mechanical automatic transmission according to the principles of the present invention.
- the electro-mechanical automatic transmission 10 is provided with a gear train 12 which includes a first input shaft 14 and a second hollow input shaft 16 which is concentric with the first input shaft 14 .
- the first input shaft 14 supports a plurality of rotatably mounted drive gears which are engaged with respective driven gears mounted to a driven shaft 18 .
- the second input shaft supports a drive gear 20 which is meshingly engaged with an idler gear 22 supported on an idler shaft 24 .
- a lay shaft 26 is provided with an input gear 28 which meshingly engages the idler gear 22 .
- a plurality of rotatably mounted drive gears are supported by the lay shaft 26 .
- a first friction clutch 30 is provided for transmitting torque from the engine output shaft (not shown) to the first input shaft 14 .
- a second friction clutch 32 is provided for transmitting drive torque from the engine output shaft to the second input shaft 16 .
- a dual cam assembly, along with first and second clutch actuators are provided for selectively disengaging the first and second friction clutches 30 , 32 .
- Commonly assigned U.S. Pat. No. 5,966,989 discloses an exemplary dual cam assembly 24 and clutch actuator system which can be utilized for selectively disengaging the first and second friction clutches 30 , 32 , as is fully described in the referenced U.S. Pat. No. 5,966,989 which is herein incorporated by reference herein.
- the gear train 12 includes second 36 , fourth 38 , and sixth 40 speed gears which are rotatably mounted to the first input shaft 14 .
- a second-fourth synchronizer device 42 is provided for selectively engaging the second and fourth speed gears 36 , 38 , respectively to the first input shaft 14 .
- a sixth speed/hill holder synchronizer device 44 is provided for selectively engaging the sixth speed gear 40 to the first input shaft 14 .
- the sixth speed/hill holder synchronizer 44 engages an overrunning one-way clutch (hill holder) device 46 for preventing the vehicle from rolling backward down a hill.
- the function of the hill holder device is described in detail in the aforementioned U.S. Pat. No. 5,966,989.
- First 48 , third 50 , fifth 52 , and reverse 54 speed gears are rotatably mounted to the lay shaft 26 .
- a first-third synchronizer device 56 is provided for selectively engaging the first and third speed gears 48 , 50 , respectively, to the lay shaft 26 .
- a fifth/reverse synchronizer device 58 is provided for selectively engaging the fifth speed gear 52 and the reverse gear 54 to the lay shaft 26 .
- the output shaft 18 is provided with a first driven gear 60 which is meshingly engaged with both the first speed gear 48 and the second speed gear 36 .
- the driven shaft 18 is provided with a second driven gear 62 which is meshingly engaged with the third speed gear 50 and fourth speed gear 48 .
- the output shaft 18 includes a third driven gear 64 which is meshingly engaged with the fifth speed gear 52 and the sixth speed gear 40 .
- a reverse idler gear 66 is provided in meshing engagement with the reverse gear 54 and also meshingly engages a reverse driven gear 68 mounted to the output shaft 18 .
- the reverse idler gear 66 also drives a low pressure lubrication pump 69 .
- the lay shaft 26 is closer to the output shaft 18 than the first input shaft 14 .
- first, third, and fifth drive gears 48 , 50 , 52 are smaller than the second, fourth, and sixth gears 36 , 38 , 40 , respectively.
- the output shaft 18 is provided with an output gear 70 which meshingly engages with a ring gear 72 of a front differential assembly 74 .
- the front differential assembly 74 is provided with left and right drive axles (not shown) as is well known in the art.
- the first input shaft 14 is supported by a bearing assembly 76 .
- the second input shaft 16 is supported by a bearing assembly 78 .
- the lay shaft 26 is supported by first and second bearing assemblies 80 , 82 .
- the output shaft 18 is supported by first and second bearing assemblies 84 , 86 .
- the idler shaft 24 is supported by first and second bearing assemblies 88 , 90 .
- the reverse idler gear 66 is supported by bearing assembly 92 .
- FIG. 2 shows a schematic view of the layout of the electro-mechanical automatic transmission for use in a front wheel drive vehicle according to the principles of the present invention.
- the first and second input shafts 14 , 16 rotate about the axis A.
- the lay shaft 26 rotates about axis B.
- the output shaft 18 rotates about axis C.
- the idler shaft 24 rotates about the axis D.
- the reverse idler gear 66 rotates about the axis E.
- the front differential assembly 74 rotates about the axis F.
- the shift rails 96 , 98 for the first and second synchronizers 42 , 44 and the shift rails 100 , 102 for the synchronizer devices 56 , 58 are also shown.
- the shift motors 104 , 106 associated with the shift rails 96 - 102 are also shown.
- First and second clutch motors 108 , 110 are also included.
- a transmission controller 120 is provided for operating the clutch actuators 122 , 124 and the shift actuators 126 , 128 .
- the transmission controller 120 provides signals to the driver motors 108 , 110 of the clutch actuators 122 , 124 as well as to the driver motors 104 , 106 of the shift actuators 126 , 128 .
- the transmission controller 120 also monitors the position of the clutch actuators 122 , 124 as well as the shift actuators 126 , 128 via potentiometers 125 , 127 , respectively. Uninterrupted power shifting between gears is accomplished by engaging the next desired gear prior to a shift event.
- the transmission 10 of the present invention can be in two different gear ratios at once, with only one clutch 30 , 32 being engaged for transmitting power. In order to shift to a new gear ratio, the current driving clutch will be released via the corresponding clutch actuator, and the released clutch will be engaged via the corresponding clutch actuator.
- the two clutch actuators perform a quick and smooth shift as directed by the transmission controller 120 which monitors the speed of the input shafts 14 , 16 via speed sensors 130 , 132 , respectively, as well as the speed of the output shaft 18 as detected by a speed sensor 134 .
- the controller 120 can determine the speed of the input shafts 14 , 16 based upon the known gear ratio and the speed of the output shaft 18 as detected by sensor 134 .
- An engine speed sensor 136 is also provided and detects the speed of the engine flywheel 137 .
- the transmission controller 120 Based upon the accelerator pedal position as detected by a sensor 138 , the vehicle speed, and the current gear ratio, the transmission controller 120 anticipates the next gear ratio of the next shift and drives the shift actuators 126 , 128 , accordingly, in order to engage the next gear ratio while the corresponding clutch actuator is in the disengaged position.
- the corresponding input shaft or lay shaft which is disengaged from the engine output shaft becomes synchronized with the rotational speed of the output shaft 18 .
- the clutch which is associated with the current driving input shaft is disengaged and the other clutch is engaged in order to drive the input shaft associated with the selected gear.
- the hill holder mechanism 46 is selectively engaged when the transmission is in first, second, or third gears in order to prevent vehicle rollback on a hill when a vehicle is at rest. Accordingly, the transmission controller 120 determines when the vehicle operating parameters are such that the hill holder features is desirable.
- the housing of the front differential 74 is provided with a plurality of projections 150 which are selectively engaged by a brake mechanism 152 which is actuated by the controller 120 to provide a parking brake feature.
- a similar brake mechanism 152 is disclosed in U.S. Pat. No. 5,966,989.
- Lubricating oil is provided to each of the drive gears via passages 154 , 156 provided in the first input shaft 14 and the lay shaft 26 .
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Abstract
Description
Claims (6)
Priority Applications (1)
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US09/506,965 US6397692B1 (en) | 2000-02-18 | 2000-02-18 | Electro-mechanical automatic transmission for front wheel drive |
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US09/506,965 US6397692B1 (en) | 2000-02-18 | 2000-02-18 | Electro-mechanical automatic transmission for front wheel drive |
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US09/506,965 Expired - Lifetime US6397692B1 (en) | 2000-02-18 | 2000-02-18 | Electro-mechanical automatic transmission for front wheel drive |
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Cited By (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6463821B1 (en) * | 2001-06-29 | 2002-10-15 | Daimlerchrysler Corporation | Method of controlling a transmission having a dual clutch system |
US20020178856A1 (en) * | 2001-06-04 | 2002-12-05 | Masami Oguri | Automatic transmission |
US6499370B2 (en) * | 2001-01-10 | 2002-12-31 | New Venture Gear, Inc. | Twin clutch automated transaxle with motor/generator synchronization |
US20040206198A1 (en) * | 2002-10-05 | 2004-10-21 | Dave Coxon | Relating to gearboxes |
US20040261555A1 (en) * | 2003-06-25 | 2004-12-30 | Janson David Allen | Layshaft automatic transmission having power-on shifting |
US20040266584A1 (en) * | 2003-06-25 | 2004-12-30 | Janson David Allen | Method for controlling speed ratio changes in a layshaft automatic transmission having power-on shifting |
US6869382B2 (en) | 2003-05-07 | 2005-03-22 | Daimlerchrysler Corporation | Double-downshift gear strategy for a dual clutch automatic transmission |
FR2881804A1 (en) * | 2005-02-09 | 2006-08-11 | Renault Sas | Double clutch transmission for motor vehicle, has one input shaft carried by another input shaft using connection system that includes ball bearings integrated to shafts and having inner ring mounted on latter shaft and outer ring |
US20080127759A1 (en) * | 2006-12-04 | 2008-06-05 | C.R.F. Societa Consortile Per Azioni | Gearbox with six or more forward gears for single-clutch or twin-clutch motor-vehicle transmissions |
US20080153666A1 (en) * | 2004-09-24 | 2008-06-26 | Volkswagen Aktiengesellschaft | Transmission configuration and method for controlling a transmission |
GB2465978A (en) * | 2008-12-03 | 2010-06-09 | Gm Global Tech Operations Inc | Gearbox with synchronizers on input shaft to reduce inertia |
US20100286943A1 (en) * | 2005-04-06 | 2010-11-11 | Battelle Energy Alliance, Llc | Method and system for detecting an explosive |
CN102135172A (en) * | 2010-01-27 | 2011-07-27 | 通用汽车环球科技运作有限责任公司 | Lubrication of a rotatable shaft |
CN101782146B (en) * | 2009-12-23 | 2012-09-05 | 黑龙江顶级汽车维修技术服务有限公司 | Power-ceaseless gear transmission |
US20150012191A1 (en) * | 2013-07-05 | 2015-01-08 | Honda Motor Co., Ltd. | Automatic transmission |
US20160116062A1 (en) * | 2013-06-11 | 2016-04-28 | Volvo Truck Corporation | Vehicle transmission and a method for operating a vehicle transmission |
CN106945500A (en) * | 2017-01-23 | 2017-07-14 | 重庆蓝黛动力传动机械股份有限公司 | A kind of speed change gear for motor vehicle driven by mixed power |
CN108397522A (en) * | 2018-04-25 | 2018-08-14 | 重庆青山工业有限责任公司 | The speed changer of oily electricity combination drive automobile |
CN108644339A (en) * | 2018-04-25 | 2018-10-12 | 重庆青山工业有限责任公司 | Hybrid vehicle multi-shifting speed variator |
US20220381322A1 (en) * | 2020-10-28 | 2022-12-01 | Dana Automotive Systems Group, Llc | Vehicle system with multi-speed transmission |
WO2023109838A1 (en) * | 2021-12-14 | 2023-06-22 | 全忠毅 | Transmission |
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- 2000-02-18 US US09/506,965 patent/US6397692B1/en not_active Expired - Lifetime
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US20080127759A1 (en) * | 2006-12-04 | 2008-06-05 | C.R.F. Societa Consortile Per Azioni | Gearbox with six or more forward gears for single-clutch or twin-clutch motor-vehicle transmissions |
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